Rotary multi-flow pump or compressor



Sept. 20, 1966 K. EICKMANN ROTARY MULTI-FLOW PUMP OR COMPRESSOR Filed' June 4, 1965 2 Sheets-Sheet l INVENTOR KAR/ E/C/(M/V/V ATTORNEY Sept. 20, 1966 K. EICKMANN 3,273,511

ROTARY MULTI-FLOW PUMP OR COMPRESSOR Filed June 4, 1965 2 Sheets-Sheet 2 3 69 f3 INVENTOR KAR/ E/C/(MAN/V 69 Z7 g AJ 34 we Hg' 4' 65 53 BY /iAA E ATTORNEY United States Patent C) 3,273,5ll RUARY MUL'fl-FLW PUMP 0R CUMPRESSR Karl Eichmann, 242@ lsshilri, Hayama-maclii, Kanagawa-ken, )Japan Filed .Brune d, 1963, Ser. No. 285,259 Claims priority, application Germany, .lune 12, 1962, E 23,017 10 Claims. (Cl. HB3-461) The present application is a continuation-in-part application of my copending application Serial No. 216,796 led August 14, `i962.

The present invention relates to rotary machines wherein a plurality of hydraulic or pneumatic flows are produced and more particularly to a rotary pump or compressor wherein at least one flow of fluid enters the rotor while at least two iiows oi fluid leave the rotor and wherein valves are opening and closing during rotation of the rotor before and after the fluid enters the working chambers of the machine or discharges therefrom.

The term fluid is used to denote `any machine, pump, or compressor driven by gaseous or liquid huid or producing flows of gas or liquid. The quantity of the at least two Hows of fluid or of the plurality of flows of fluid leaving the machine is preferably proportional.

The working chambers in the pump or compressor which during rotation of the rotor are periodically increasing and decreasing its volume if the machine delivers flows of uid may be cylinders, may be intervane spaces, may be gear pump spaces, Vmay be trochoid piston spaces or the like.

lt is one object of the present invention to provide a rotary pump or compressor wherein at least two or a plurality of flows are produced in the rotor of the machine or wherein a flow of fluid is divided into a plurality of flows of fluid inside of the rotor of the machine.

Another object of the invention is to eliminate communication between two or more of the plurality of ows which are created in the rotor of the machine.

Another object of the invention is to provide a plurality of flows in the rotor of the machine which are capable also of high or very high pressure, or to increase the pressure in at least one of such flows.

Another object of the invention is to eliminate losses in the delivery quantity or leakage of relatively higher pressure to relatively lower pressure flows in multiflow pumps or compressors.

Still a further object of the invention is to provide eilicient sealing means which are able to follow inaccurate movement of the rotary tubes for sealing the rotary entrance or exit ports of the machine.

And another object of this invention is to provide at least one rotary entrance passage for the entrance of fluid into the rotor and to provide at least two rotary exit passages for the ilow of fluid out of the rotor of the machine.

With these objects in view, one embodiment ofthe present invention relates to a machine which comprises a rotor, and means forming in the rotor at least two working chambers, expanding and contracting during rotation of the rotor and communicating with different and from each other separated passages for the inlet and outlet of fluid. Inlet valve means are located in the inlet passage or in the inlet passages. Outlet valve means are located in the outlet passages. At least one inlet passage is located in the rotor, leading from the rotary entrance port to the inlet valve means. A stationary entrance port is also provided on the machine, leading to a stationary entrance chamber. A sealing means is provided between the stationary entrance chamber and the rotary entrance port. At least one rotary tube is provided in the rotor. Said at least one rotary tube contains at least two delivery passages. The said two delivery passages are separated from each other. At least a first and a second stationary exit port is provided on the machine. Each of the said stationary exit ports leads to a respective stationary exit chamber. The rst exit passage leads from the delivery or discharge valve means or valves of the respective working chamber or working chambers, which produces or produce the rst ow of fluid, through the said rotary tube or tubes to the rst stationary exit chamber.

The second exit passage leads from the delivery or discharge valve means or valves of the respective Working chamber `or working chambers which produces or produce the second flow of fluid, through the said rotary tube or tubes to the second stationary exit chamber. Seal means are provided around the rotary tube or tubes for sealing each of the said stationary exit chambers against other stationary exit chambers or against the stationary entrance chamber -or against other chambers or spaces in the machine. One or more additional exit ports, stationary exit chambers, rotary tubes, passages, sealing means or working chambers can be provided for the producing, guiding, passing or sealing for or of additional flows of liquids or gases. The rotary tube can consist of a plurality of rotary tubes whereof at least one of the rotary tubes may be provided centrically inside of another or others of rotary tubes.

A prefered embodiment of the said seal means consists each of a seal bush which is provided with a cyindrical inner face which surrounds and seals the outer face of a rotary tube. The small clearance between the said faces provides the seal from one axial end of the seal bush to the other. The seal bush is provided with two primary radialwards extending pin means. Said primary pin means extend into dimetrically located bores or slots of a free floating ring. Secondary pin means are located in bores or slots of said free floating ring and extend radially outwards into the surrounding housing or seal housing member. Axialwards extending slots are provided in said seal bush, free floating ring, seal housing or seal housing member for the provision of the ability for axial movement of one or some of the cooperating parts of the said seal bush, free oating ring or primary or secondary radialwards extending pin means or casing.

A support ring is provided between a spherical backwards face of the respective seal bush and a radial plane face of the adjacent seal housing or seal housing member. Said support ring is provided with a radial plane face on one axial end and a spherical face on the oppositional axial end thereof. The radial plane face of the respective support ring is borne on the plane of the seal housing or seal housing member and is able to slide radially thereon. The backwards spherically or spherical face of the respective seal bush is borne on the spherical face of the respective support ring and able to swing or slide spherically thereon.

The novel features which are considered as characteristics of the invention are set forth in particular in the appended claims. The invention itself, however, both to its construction and its method of operation, together with additional objects and advantages thereof will be best understood from the following description of specific embodiments when read in connection with the accompanying drawings in which:

FIG. l is a longitudinal sectional view illustrating one embodiment of a rotary pump or compressor in accordance with the present invention;

FIG. 2 is a cross sectional view taken on line lI-II of FlG. l;

FIG. 3 is a cross sectional View through FIG. 1 taken along the line lll-III;

FIG. 4 is a cross sectional partial view taken along line IV-IV of FIG. 3.

A rotary multiflow pump or compressor in accordance with the present invention is illustrated in FIGURES 1 and 2 by way of example.

A rotor 40 is turna'bly supported in bearings 41 and rotates, for example, in the direction of the arrow L shown in FIGURE 2. Rotor 40 has a drive shaft 51 which may be driven by the output shaft of the prime mover, not shown, Iand coupled to the said drive shaft 51 by key means located in the key way 52.

Rotor 40 is formed with a plurality of working chambers or cylinder cavities 35 in which pumping means or pistons 50 are mounted for sliding movement in the said working chambers. Piston pins 36 are inserted into piston 50 and extend perpendicular to the axis of the respec tive piston 50 and cylinder 35. The ends of piston pins 36 extend into bores in piston supports 37 which are guided on guide faces of a rotary guide case 38.

Guide case 38 is supported for turning movement in bearings 42 which are excentrically arranged with respect to the axis of rotor 40 by means of members 39 whose position may be adjusted by the control member 46. Guide case 38 is located within a housing 44.

At least one or a plurality of rst ow discharge passages 44 and at least one or a plurality of second ow discharge passages 45 which might be inclined .to the axis of the rotor, or which might also be radially to the axis of the rotor are yconnected to respective working chambers 35.

A rotary inlet chamber 5 is provided in rotor 40. Inlet valve means are located between said rotary inlet chamber 5 and the respective working chamber or working chambers 35. Outlet 0r discharge valve means are located between the respective working chamber or chambers 35 and the trst ow discharge passage or passages 44 or between the working chamber 35 and the second flow discharge passage or passages 45. The said inlet valve means may consist of a valve case 1 which is provided with a guide Way 31. A valve member 7 is located in guide way 31 and able to reciprocate therein. Valve member 7 is provided with a passage or passages 9. A pivot pin 3 is loca-ted in case 1 and a control lever member 4 is supported on pivot pin 3 and able to pivot around the axis of pivot pin 3. A recess or recesses 10 is or are provided in valve case 1 for the communication of the passage 9 wi-th the rotary inlet chamber.

The outlet means may consist of a valve case 12 which is provided with la guide way 19. A-valve member 15 is located in guide way 19 and able to reciprocate therein. Valve member 15 is provided with an inner passage 18.

Valve seats 11 are provided on valve case 1 and on valve member 7. If the inlet valve means is closed then valve seat 11 of valve member 7 is borne by valve seat 11 of valve case 1 and sealing respectively thereon. The valve seats 11 prevent any backwards ow of fluid out from the respective Working chamber 35 into the respective passage 9 or into the rotary inlet chamber 5. Valves seats 17 are provided on Valve case 12 and on valve member 15.

If the outlet or discharge valve means is closed then the valve seat 17 of valve member 15 is borne on the valve seat 17 of valve case 12 and seals thereagainst. The closed valve seats 17 of valve member 15 and valve case 12 prevent any leakage or flow of fluid out from the respective rst flo-w discharge passage or passages 14 into working chamber 35 or out from the second ilow discharge passage or passages 45 into the respective working chamber or working chambers 35.

A plurality of rotary tubes is provided in or on rotor 40. The rotary inlet Itube 48 surrounds the rotary inlet passage 62. Compressor vanes 49 are secured to rotary inlet tube 48 and draw uid into the inlet duct or into the rotary inlet passage 62 during rotation of the rotor. The rotary inlet tube 48 is preferably integral with rotor 4 4t?. A ilow inlet passage or inlet duct or liow inlet passages 6 extends or extend from the rotaly inlet passage 62 into the rotary inlet chamber 5. Rotary delivery tubes are inserted into the rotary bore i-n rotor 4th and secured in the rotor by the transverse pin 53.

As will be seen from the FIGURE 1 the valve seats of the inlet and outlet valves form inlet and outlet openings of the working chambers and the valve members 7 and 15 are guided in the respective valve cases outside of the respective working chamber .so that the dead space in the working chamber is a minimum and losses due to inner compression of the fluid are narrowed or avoided.

When rotor and guide case 38 are rot-ated by a prime mover, acting on drive shaft 51, while the axis of guide case 38 is maintained in an excentric position with respect to the rotor axis, uid flows into rotor 40 through the inlet tube 48 since in :the suction zone of -the pump the pumping means or pistons 58 are retracting and the respective working chamber or chambers 35 expands or are expanding.

The uid enters the recess 1@ of the cases of the inlet valve, ows partly around the valve stem and enters into passage 9 of the respective inlet valve or valves.

While pumping mean constituted by piston or pistons 5@ move outwardly on the suction side of the rotary uid pump or compressor, the valve seat 11 of the inlet valve means lopens and the flow Hows from passage 9 through the inlet valve means seat 11 into the expanding working chamber 35.

At the same time, other pistons 5t) advance so that the working chamber or chambers or cylinders 35 on the discharge side of the rotary multitlow pump or compressor contract and discharge fluid through the discharge valves which open due to the pressure on the valve heads of valve members 15.

When the respective pumping means or piston reaches its outwardly located dead center position at the end of the suction stroke, the working chamber 35 is lled with uid and the flow of fluid stops. The control lever member 4 of the suction valve means closes the valve seat 11 of the suction valve means by retracting the valve member 7 to the right thereby closing the valve seat 11.

During the inward movement of the respective pumping means or piston 50 the fluid in the respective working chamber 35 is subjected to increased pressure, and as soon as .the fluid pressure in the working chamber, acting against valve member 15 is substantially higher than the pressure in the discharge passage 44 or 45 which acts against valve member 15, the respective discharge valve member 15 is moved inwardly and the outlet or discharge valve is opened. Thereby valve member 15 of the outlet valve means moves with its valve seat 17 away from the valve seat of valve case 12 and uid can ow out of the working chamber 35 through valve seats 17 and through the inner passage 18 of the respective valve member 15 into the respective rst flow discharge passage 44 or into the second flow discharge passage 45.

When the respective piston 5@ arrives in its inner dead center position, the flow of fluid stops and the centrifugal force acting on the discharge valve member 15 moves the discharge valve member outwardly Ito the valve closing position so that valve seats 17 are closed.

Valve case 1, head 2, pivot pin 3, control lever member 4, valve member 7, flow inlet passage or inlet duct 6, valve member '7, passage 9, valve seat 11, valve case 12, valve member 15, valve seat 17, inner passage 18, guide way 19, guide way 31, piston pin 36, piston support 37, guide case 38, members 39, rotor 41B, bearings 41, bearings 42, housing 43, control member 46, rotary inlet tube 48, and compresser vanes 49 are known and in detail described in my copending patent application Ser. No. 216,796, tiled August 14, l962. y

Also already known from my copending patent applications are cylinders 35' and pistons 50 as well as discharge passages 4d or 45.

But the working chambers 35 of this invention are defined thereby that they do not necessarily have to be cylinders. On the contrary they may be intervane spaces, trochoid piston pump or compressor spaces, gear pump spaces or the like, depending on the actual design. Therefore, also the pumping means of this invention need not necessarily be pistons but may also be gears, vanes, trochoid curved pistons, or the like.

The first flow discharge passage or passages 44 and the second tlow discharge passage or passages 45 are objects and means of this invention and theyare differing from the discharge passages 44 or 45 of my said copending patent applications therein, that the first tlow discharge passage or passages i4 extend from the respective discharge valve means to the inner delivery passage 3) through rotary ring channel 63 of this invention while the second ilow discharge passage or passages d5 extend from the respective outlet or discharge valve means to the outer delivery passage 29 through the rotary ring channel 6ftof this invnetion and thereby that the first flow discharge passages 4d do not communicate with the second fiow discharge passage 45 but on the contrary that the first flow discharge passage or passages dd is or are separated in accordance with this invention from the second flow discharge passage or passages d5.

Rotor d@ is provided with at least one rotary tube. rThe rotary tube or tubes are inserted into the rotor hub or rotor center bore and extend axially beyond rotor d0.

ln the figures the rotary tubes are `consisting of the outer rotary delivery tube i4 and the inner rotary delivery tube i3. The outer rotary delivery tube 14 is provided with the outer tube seat member lil. The inner rotary delivery tube 13 is provided with the inner tube seat member E. Both seat members 3 and itl are fitting inside of the rotor center bore or rotor hub.

The inner rotary delivery tube 13 is surrounded from the outer rotary delivery tube i4 or the inner rotary delivery tube i3 is located inside of the outer rotary delivery tube ld. The inner rotary delivery tube i3 extends axialward-s beyond the outer rotary delivery tube ld. Between the outer rotary delivery tube ld and the inner rotary delivery tube 13 is the outer' delivery passage 29 provided. ln the inner rotary delivery tube i3 is the inner delivery passage 3i) located.

The inner rotary delivery tube i3 is provided with rotary tube ports 2t) and 23. The outer rotary delivery tube llt is provided with rotary tube ports 2li and 22.

Axially backwards on housing d3 is the seal housing 24 provided. The seal housing 24 is provided with at least `one stationary entrance port 25 and at least two stationary exit ports 26, 27. ln FGURE l, the first stationary exit port 26 and also the second stationary exit port 27 are shown. ln seal housing 24 is also the stationary entrance chamber 28 provided. The seal housing 2d is also provided with a plurality of stationary exit chambers. FIG- URE l shows the first stationary exit chamber 32 and a second stationary exit chamber 33.

The rst stationary exit port 26 extends into the first stationary exit chamber 32 while the second stationary exit port 27 extends into the second stationary exit chamber 33.

lt should be noted that instead of two exit ports and two stationary exit chambers there might also be a greater number of exit ports and exit chambers provided on and in the seal housing 24. At least each separated stationary exit chamber is provided with at least one stationary exit port.

At least one rotary tube extends into or through the respective stationary exit chamber. Each stationary exit chamber is sealed against other spaces except against the rotary tube port or ports or stationary exit port or ports which extend into the stationary exit chamber. Sealing means are provided around the respective rotary tube withti in the seal housing 24 for sealing the respective stationary exit chamber in axial direction,

Rotary tube port or ports 2t) are provided through the rotary tube between the inner delivery passage 30 and the first flow discharge passage or passages 44 and they are thereby providing the passage from the first fiow discharge passage or passages 4d into the inner delivery passage 3).

The rotary tube ports 2l are provided through the outer rotary delivery tube ld between the outer delivery passage 29 and the'second fiow discharge passage or passages 035 thereby providing the passage between the second flow discharge passage or passages d5 and the outer delivery passage 29.

A ring space 63 is provided in rotor 40 or in the respective rotary tube for the collecting of fluid out from the first ow discharge passages 44 and/ or for communication of the plurality of first fiow discharge passages lll if a plurality of first flow discharge passages is provided.

Another rotary ring space d4 is provided in rotor 40 or in the respective rotary delivery tube lll for the collection of the fiuid out from the second :flow discharge passages lt-t or for the communication of a plurality of second fiow discharge passages t5 it a plurality of second flow discharge passages d5 is provided in the rotary pump or compressor.

The rotary tube port or ports 22 are provided through the outer rotary delivery tube ld between the outer delivery passage 29 and the first stationary exit chamber 32 thereby providing a passage or passages between the outer delivery passage 29 and the first stationary exit chamber 32.

The rotary tube port or ports 23 are provided through the inner rotary delivery tube i3 between the inner delivery passage Sti and the second stationary exit chamber 33 thereby providing a passage or passages between the the inner delivery passage 3ft and the second stationary exit chamber 33.

Seal means, for instance, plastic seal means or seal rings 16 may be provided between rotor tti and the rotary tubes. More in detail a seal ring i6 may lbeprovided leftwards ofthe rotary tube ports 2t), a seal ring means i6 may be provided in the inner tube seat member S and a seal ring means .t6 may also be provided in the outer seat member liti.

The inner tube seat member tt separates the rotary tube ports 2t? from the rotary tube ports 2l and thereby also seals and separates the first fiow discharge passage i4 from the second delivery rlow.

The outer tube seat member lil separates the rotary tube ports 2l from the rotary inlet passage 62 or liow inlet passage or passages 6 and thereby the second delivery fiow from the entrance dow.

In the cross sectional view which is demonstrated in FIGURE 2 it will be seen that the multiliow pump of this embodiment is provided with l0 pistons 50A, 50B, 50C, 50D, 50E, StiF, EtlG, Stil-l, 50K, and SGL. The pistons 50A are located in the respective cylinders 35A, 35B, 35C, 355D, 35E, 351:, 3BG, 35H, 35K, and SSL.

The cylinders 35A, 35C, 35E, SSG, and 35K are the working chambers of the first flow working chamber group according to this invention. The cylinders 35B, 35D, 35i?, 35H, and SSL are the working chambers of the second flow delivery working chamber group in accordance with this invention.

lt is therefore clearly visible that each .one working chamber of the second flow working chamber group is located between two working chambers of the `first working chamber group and vice versa.

Each cylinder or Working chamber of the first working chamber group is provided with a first flow discharge passage 44 of this invention. On the -contrary thereto each working chamber of the second tlow working charnber group is provided with a second iiow discharge passage d5.

It Will therefore be seen from FIGURE 2 that working chambers 35A, 35C, 35E, SEG, and 35K, are provided with lirst flow discharge passages 44 while on the contrary the working chambers 35B, 35D, 35E, 35H, and SSL are provided with second ilow discharge passages 45.

Between the said rst iiow or second iiow working chambers and the said irst flow discharge passages or second flow discharge passages are, as already described above, the outlet or discharge valves means provided and may extend into said discharge passages.

Thus, in accordance with this invention, if rotor 4@ revolves and the axis of guide case 38 is eccentrically spaced from the axis of rotor 40, and the rotor revolves for instance in the direction of arrow L in FIGURE 2, then uid enters through the stationary entrance port 25 into the stationary entrance chamber 28, therefrom along compressor vanes 49 into the rotary inlet tube 48 and through the rotary inlet passage 62, thereafter through flow inlet passages or inlet ducts 6 into the rotary inlet chamber and thereout into the respective recesses it) of the valve cases l, thereafter through passage 9 and valve seat Il into the respective working chamber 35 when the said working chambers 35 increases its volume.

In the FIGURE 2 is the suction zone, wherein the respective working chambers 35 are increasing, shown on the right side of the figure while on the left side of the figure the discharging side, wherein the respective working chamber are decreasing their volume, is demonstrated. Working chamber 35A is in the outer dead center while working chamber SSF is in the inner dead center.

The cylinders and pistons in the inner and outer dead centers are not in the suction zone, nor in the delivery or discharge zone, but between these said zones. Working chambers SSG, 35H, 35K, and 3SL, are therefore in the suction zone of FIGURE 2 while working chambers 35B, 35C, 35D, and 35E, are in the delivery zone of the notary pump of FIGURE 2.

The ow of fluid from the stationary entrance port into the respective working chambers 35 appears only in the suction zone of the rotary pump or compressor. In the contrary thereto the delivery i'lows are appearing only in the discharging or delivery Zone of the rotary pump or compressor.

In the delivery Zone of the multiow rotary pump or compressor of this invention, when the respective pumping means or pistons 50 are compressing the uid in the respective working chambers or cylinders 35, the outlet or discharge valve means opens and the iiow ilows out of the respective working chamber of the first ow working chamber group through the respective valve seat or seats 17, thereafter through the respective inner passage or passages 18 of valve member l5 into the respective iirst ilow discharge passage 44 or into the respective first flow discharge passages 44, therefrom into the rotary ring groove 63, thereout through the rotary tube ports 2G into the inner delivery passage 30 and thereby through the inner rotary delivery tube i3 thereafter out of the inner rotary delivery tube 13 through the rotary tube ports 23 into the second stationary exit chamber 33 and out therefrom into the second stationary exit port 27 wherefrom the first liow of fluid may be passed into respective pipes or tubes which can be connected to the second stationary exit port 27.

On the contrary thereto, the delivery tlow out of the second flow working chamber in the delivery zone ows from the respective working chamber 35 through the valve seat 17 and through the respective inner passage or passages 18 of valve member i5 into the respective second ow discharge passage or passages 45 and out therefrom into the rotary ring groove 64, out therefrom through the rotary tube ports 21, thereafter through the outer delivery passage 29 and thereby through the outer rotary delivery tube 14, thereafter out from the outer delivery passage 2.9 through the rotary tube port or ports Z2 into the rst stationary exit chamber 32 and out therefrom into the first stationary exit port 25. From the first stationary exit port 26 the first ow of uid may be or may pass into pipes or tubes which can be connected to the rst stationary exit port or ports 26.

The flow out from the respective iirst iiow Working chamber group to the second stationary exit port 27 is the first delivery flow of the rotary multiilow pump or compressor. The flow of uid out from the respective working chambers of the second working chamber group to the first stationary exit port 26 is the second delivery flow of the rotary multiow pump or compressor.

The first delivery ow and the second delivery ow appears only out from such working chambers which are in the delivery or discharge zone of the rotary multiilow pump or compressor.

In FIGURE 2 working chambers 35C, and 35E, it they are in the position as shown in FIGURE 2, are pro' viding the rst delivery ow.

On the contrary thereto in FIGURE 2 the working chambers 35B and 35D are, if they are in the position as shown in FIGURE 2, providing the second delivery flow yof the rotary multiflow pump or compressor.

The embodiment of the rotary fluid machine shown in FIGURES 1 and 2 is a rotary two-How pump or a rotary two-flow compressor.

But the rotary multiflow pump or compressor of this invention is not limited to two-flow pumps or compressors. Instead of this, three, four yor more delivery flows can be provided in respectively designed .o1- built rotary multiow pumps or compressors.

For instance, instead of providing only first stationary exit ports and second stationary exit ports it will also be possible to provide also third and fourth or a multiple of stationary exit ports. Instead of providing only an inner and an outer rotary delivery tube it would also be possible to provide a plurality of rotary delivery tubes and plurality of different delivery passages therein. Instead of providing only first flow discharge passage and second flow discharge passage, it is also possible to provide a plurality of different ow discharge passages in the rotor of the rotary multiflow pump .or compressor.

All such different iow are preferably separated from each other and sealed against each other.

Between each set of a group of flow discharge passages and the thereto belonging stationary exit ports must be a respective stationary exit chamber and at least a respective delivery passage through a rotary delivery tube be provided and respective rotary tube ports must provide the communication and passage between the respective delivery passages and the respective stationary exit chambers and between the respective delivery passages and the respective flow discharge passage.

The inner rotary delivery tube 13 and the outer rotary delivery tube 14 are provided with cylindrical outer faces 65. In both axial directions of the rotary tube port or ports 22 and also in both axial directions of the rotary tube ports 23 are each one seal bush 3dprovided. Each seal bush 34 is provided with a cylindrical inner face 35. The seal bushes are surrounding the respective rotary delivery tubes and between the respective cylindrical inner face and the respective cylindrical outer face is a very small clearance provided which provides the seal in axial direction between the respective seal bush 34 and the inner rotary delivery tube 13 or the outer rotary delivery tube 14. Each seal bush 34 is provided with a backwards spherical face 61. Backwards of each seal bush 34 is a support ring 47 provided. Each support ring 47 has a spherical face 59 on the one axial end and radial plane face 58 on its other axial end. On both axial ends of each of the stationary exit chambers are respective seal housing members 67 provided. Each seal housing member 67 is provided with a radial plane face 60.

The said support rings 49 are adapted against the said seal housing members 67.

Therefore the backwards spherical face of the respective seal bush 34 is borne on the spherical face of the respective support ring 49 and the radial plane face 58 of the respective `support ring 47 abuts on the respective radial plane face 60 of the respective seal housing member 67. The said radial plane faces are able to slide radially along each other and they are sealing against each other while the said spherical faces are able to slide spherically along each other and are sealing each other.

Spring means 57 can be provided between the two seal bushes 34 of the respective stationary exit chamber and they are pressing the respective seal bushes 34 against the respective support rings 49 and the said support rings against the respective seal housing members 67 thereby assuring the seal between the respective seal bush, support ring and seal housing member. Pressure in fluid in the respective rst stationary exit chamber or of the second stationary exit chamber may assist the action of the said spring means 57.

The combination of the seal housing members, support rings 49 and seal bushes 34 makes it possible that the respective seal bushes 34 follow all inaccurate movements the respective rotary delivery tube and thereby maintaining an effective seal and preventing friction between the said cylindrical inner faces 65 of seal bushes 34 and the respective cylindrical iouter face 66 of `the respective rotary delivery tubes 13 or 14.

The seal bushes 34 may be provided with radial extending pin means 65 and the said -pin means 65 prevent the respective seal bushes 34 from rotation around its axis.

Drain passages 55 and 56 can be provided through the seal housing 24 for the passage of drain from the backwards spaces on ends of the respective seal bushes. The drain passages may extend out from the fluid machine or they may extend into the inner space in housing 43 of the rotary pump or compressor.

The seal bushes, support rings, and the other seal means around the rotary delivery tubes and the sealing means of the stationary exit chambers are known and/or more in detail described in my United States Patent 3,070,377.

However, the seal means contained in seal housing of this invention are an improvement 4over my said United States Patent 3,070,377. The improvement consists therein, that the axial movability of the seal bush 34 is more definitely assured by this invention while at the same time the floating condition of the seal bush 34 and of the floating ring 47 is effectively improved.

In detail, the improvement consists therein that primary radialwards extending pin means 68 are provided on the respective seal bush 34 and that secondary radialwards extending pin means 69 are extending into the seal housing 24. Each seal bush 34 is provided with two radialwards extending pin means 68. The said primary radial extending pin means 68 are diametrically located `with respect to Athe axis of the respective seal bush 34 and have a common axis.

The axis of the said primary radial extending pin means is perpendicular to the axis of the secondary radial extending pin means 69. The secondary radialwards extending pin means are extending into the seal housing 24 or are retained therein.

A floating ring 53 is provided between the respective seal bush 34 and the seal housing 24. Space is provided between the inner diameter of floating ring 53 and the outer diameter of the seal bush 34 while also space is provided between the outer diameter of floating ring 53 and the inner diameter `of the respective part .of the seal housing 24. The floating ring 53 is therefore able to move radially outwards and inwards in a limited extent. Each floating ring 53 is provided with diametrically located bores or slots. The primary radialwards extending pin means 68 are extending into respective diametrically located bores or slots of floating ring 53. The secondary `l0 radialwards extending pin means 69 are extending from the seal housing 24 into respective bores or `slots of floating ring 53.

Axial slots 70 are provided in seal housing 24 or in floating ring 53 or in the respective seal bush 34. The primary radialwards extending pin means lor the secondary radialwards extending pin means are able to slide axialwardly in the said axialwardly extending slots or bores 70. The desired axialwards movement of the floating ring 53 or at least of the seal bush 34 in a limited extent is thereby assured.

It should be noted that the primary radialward extending pin means -are extending into seal bush 34 and floating ring 53 or through floating ring 53 bu-t n'ot into engagement with or into the seal housing 24. In contrary thereto the secondary radialwardly extending pin means 69 are extending into or through floating means 53 or into or through seal housing 24 but not into engagement with or into the respective seal bush 34.

Since the axis of the primary pin means and of the secondary pin means are normal -to each other, each seal bush 34 is able to radialwards movement and -the floating ring 53 is mounted for pivotal or swing movement around the axis of the secondary pin means 69 while the seal bush 34 is additionally able to swin g around the axis of the primary extending pin means 68. All seal bushes 34 and oating rings 53 are also able to move along the axis of the primary and of the secondary radialwards extending pin means. Therefore the Iseal bushes 34 are able to perform all required spherial movements when the rotary pump or compressor operates. A-t the same time all sea-l bushes 34 are able to perform a limited axial movement so that the adaption of the spherical ffaces 59 and 61 against each other and of the radial plane faces 58 and 60 against each other and thereby is also the seal between the seal bushes 34, support ring 49 and seal housing member 67 definitely assured in accordance with this invention.

The seal bushes 34 are able to follow all inaccurate rotary movements of the respective rotary tube.

Smaller clearances are therefore possible between the cylindrical inner faces `35 of the lrespective seal bushes 34 and the cylindrical outer faces 66 of the respective rotary tube `due to the spherical movability of the seal bushes. The smaller clearances are reducing leakage through the clearance which appeared in former machines. The provision of the effective seal means around the rotary tubes and of the valve means in the rotor are important means for preventing leakage.

An important feature of this invention is not only the possibility to provide a rotary multiflow pump or compressor which delivers a plurality of flows, but also to deliver a plurality of flows of fluid without or with only small leakage or with substantially equal leakage of the flow-s. It is -therefore possible to deliver a plurali-ty of flows with a proportional delivery quantity from the rotary multiflow pump or compressor of this invention.

If the displacement yof the working chambers of the one of the working chamber groups are different from that of another or other working chamber groups, then the delivery quantity of the different flows lis only proportional. If all working chambers of all `working chamber groups are of equal displacement, then the delivery quantity of all flows is equal.

An important feature of this invention is, that `the sealing means and valve means of the multiple of flows of this rotary multiow pump -or compressor are in practice so perfected that the delivery of a respective flow remains rslipless or lossless regardless of whether high pressure or low pressure is present in the respective flow of uid. It is also an important feature of this invention that different pressures can be applied to different flows of fluid of the pumps or compressors of the invention. It has been proved in practical examinations of the ro-tary pump of this invention that pressures of 5000 to 6000 p.s.i. may

be delivered in one or more of the delivery ilows while atmospheric pres-sure or only a few p.s.i. may be present in another or other flows of the pump.

This makes it possible to drive different motors, pumps or the like, of machines regardless of their load or power, with proportional or equal speed. Also if the load on such different rams, motors or the like which are driven by different delivery flows of the rotary pumps of the invention is very different, the speed of such different loaded rams, motors or the like remains proportional or equal if so desired. Parallel or proportional acting multipiston presses, parallel or proportional acting arms, shovels or the like of construction machines can therefore be as well eiciently driven by this new pump or compressor as well as helicopter like planes with a multiple of lifting propellors can be kept in balance during their travel through lthe air, if driven by motors which are driven by this new pump. There are many other novel application possibilities in or on machines or vehicles or compressors, where this new yrotary multiow pump or compressor can be applied.

While earlier multiflow pumps failed to keep the parallelity or proportionality of the quantity of the delivery flows, such disadvantages have been entirely overcome by this invention.

Additionally due to the narrowing of friction losses and leakage losses the total power of the multiow pumps or compressors and i-ts total efiiciency is considerably increased by the objects and means of this invention. The ruin of machines or vehicles by leakage of one or some of higher loaded flows 'of a plurality of ows which drive machines delivering proportionality of the speed of the movement of its parts is prevented by -this invention because the slip -between the moving parts which are driven by the flows of the new pump is prevented by the prevention of leakage. The proportionality of the ows regardless how they are loaded also prevents accidents of machines or vehicles.

The valves which are applied in the embodiments of the gures are by Way of example only and so are the sealing means. If so required or suitable, it will also be possible to provide inlet or outlet or discharge valve means of other 'designs in the pump or compressor of this invention, for instance fluid ow or fluid pressure operated valve member or spring and fluid opera-ted or mechanically operated valves. Instead of seal bushes and support rings, it is also possible to provide the seal means for the seal of the rotary tubes and the stationary exit channels, for instance seal rings of plastic material, slip rings or bushes or the like. The provision of the working chambers peripherically behind each other is also by way of example only.

Instead of providing, each one working, of one working chamber group peripherially behind a working chamber of another working chamber group it would also be possible, for in-stan-ce, to provide a plurality of working chamber groups axially distanced from each other in the rotor of the pump or compressor.

The possibility to provide working chambers with different cross sections makes i-t possible to realize a different delivery, but proportional delivery while equal stroke for instance of the pistons in the working chambers remains maintained. Also the use of rotary tubes is by way of example only. Instead of the rotary tubes it would also be possible especially in pumps or compressors with less desired performances, to provide non-rotary control pintles with cylindrical, spherical, conical or plane control ports and fluid passages through said control pintle in a rotor hub, or axially on one yrotor end for cooperation with corresponding control faces and control ports on the rotor for the provision of passing at least one outlet How into the rotor and a plurality of ows out of the rotor.

It will be understood that each of the elements described above, or two or more together, may also find a useful application in other types of rotary pumps or compressors differing from the type described above. While the invention has been illustrated and described by way of description of an embodiment, it is not intended to be limited to the details shown, since various modifications and structural changes may be made without departing from the spirit Vof the present invention.

Without further analysis, the foregoing will so fully reveal the gist of the present invention that others can by applying current knowledge, readily adapt it for various applications without omitting features that, from the standpoint of prior art, fairly constitute essential characteristics of the generic or specific aspects of this invention and, therefore, should and are intended to be comprehended within the meaning and range of equivalence of the following claims.

What is claimed as new and desired to be protected by Letters Patent is:

l. In a fluid handling machine, in combination, rotormeans having an axis and including a main portion with a first diameter having a plurality of cireumferentially spaced working chambers expanding :and contracting during rotation, and inlet ducts and outlet ducts communicating with said working chambers, said rotor means having a fluid distributing portion projecting in axial direction from one axial end of said main portion and having a diameter smaller than the diameter of said main portion, said distributing portion rotating with said main portion and including a plurality of tubular members surrounding each other :and forming in and between each other an inlet passage connected with said inlet duct and a plurality of delivery passages respectively connected with selected outlet ducts whereby the iluid pressures in said delivery passages are determined by the pressures in the working chambers with which said selected outlet ducts are connected.

2. In a fluid handling machine, in combination, rotor means having an axis and including a main portion with a first diameter having a circular row of circumferentially spaced working chambers expanding and contracting during rotation, a plurality of outlet duct means respectively communicating with selected working chambers, and inlet ducts communicating with said working chambers, said rotor means having a uid distributing portion projecting in axial direction yfrom one axial end of said main portion and having a diameter smaller than the diameter of said main portion, said distributing portion rotating with said main portion and including a plurality of tubular members coaxial with said Aaxis surrounding each other and forming in and between each other an inlet passage connected with said inlet ducts and a plurality of delivery passages respectively connected with said outlet ductmeans.

3. In a fluid handling machine, in combination, rotor means having an axis `and including a main portion with a first diameter having a circular row of circumferentially spaced working chambers expanding and contracting during rotation, a plurality of outlet duct means respectively extending at different angles to said axis and respectively connected with selected working chambers, and inlet ducts communicating with said working chambers, said rotor means having a fluid distributing portion projecting in `.axial direction from one axial end of said main portion and having a diameter smaller than the diameter of said main portion, said distributing portion rotating with said main portion and including a plurality of tubular members coaxial with said axis surrounding each other and forming in and between each other an inlet passage connected with said inlet ducts and a plurality of delivery passages respectively connected with said outlet duct means; a stator supporting said rotor means for rotation about said axis, and including a casing portion surrounding :said distributing portion and forming with the same an inlet chamber having an inlet, and a plurality of dis- Charge Chambers each of which has an outlet, said inlet passage having an opening in said inlet chamber, and said delivery passages having openings, respectively, in said discharge cha-mbers whereby the iiuid pressures in said delivery passages and at said outlets of said discharge chambers are determined by the pressures in the working chambers with which said selected outlet duct means are connected; and sealing means for fluid-tightly separating said inlet chamber and said discharge chambers from each other.

4. 1n a iiuid handling machine, in combination, rotor means having an axis and including a main portion with a iirst diameter having a circular row of circumterentially spaced working chambers expanding and contracting during rotation, a plurality of outlet duct means respectively extending iat different angles to said axis and respectively connected with selected working chambers, and inlet ducts communicating with said working chambers, said rotor means having a fluid distributing portion projecting in axial direction from one axial end of said main portion and having a diameter smaller than the diameter of said main portion, said distributing portion rotating with said main portion and including a plurality of tubular members coaxial with said axis surrounding each other and forming in and between each other an inlet passage c-onnected with said inlet ducts and a plurality of delivery passages respectively connected with said outlet duct means, said tubular members 'being of different length and having axially staggered free ends, each of said tubular members having `a portion in the region of the free end thereof so that said ports are spaced in axial direction and are located outward of said free ends of tubular members surrounding the tubular member in which the respective port is located; and a stator supporting said rotor means for rotation about said axis, and including a casing portion surrounding said distributing portion and forming with the same an inlet chamber having an inlet, and a plurality of discharge chambers each of which has yan outlet, `said inlet chamber and discharge chambers being adjacent in axial direction and respectively housing said free ends of said tubular members and the respective ports, said inlet passage opening in the port in said inlet chamber and said delivery passages opening in said ports, respectively, in said discharge chambers whereby the fluid pressures in said delivery passages and at said outlets of said discharge chambers are determined -by the pressures in the working chambers with which said selected outlet duct means are connected.

5. The tiuid handling machine set forth in claim 2 wherein said outlet duct means communicate with working chambers selected so that the amounts of iiuid fiowing through said delivery passages into said discharge chambers are proportionate.

6. The iiuid handling machine set forth in claim 2 wherein said outlet duct means communicate with working chambers selected so that the amounts of iiuid iowing through said delivery passages into said discharge chambers yare equal.

7. The Huid handling machine set forth in claim 2 wherein the two innermost of said tubular members form between each other :a rst delivery passage, and the inner tubular member of said two tubular members forms a second delivery passage, said first and second delivery passages being respectively connected to a series of first outlet ducts and to a series of second outlet ducts, said first and second outlet ducts being respectively connected with alternate working chambers; and wherein said inlet passage is formed between the outer tubular member of said two tubular members `and a tubular member surrounding said last mentioned outer tubular member, and communicates with all said working chambers.

8. In a fluid handling machine according to claim 4, in combination, a sealing means in each of said inlet and discharge chambers for fluid tightly separating the same from each other, each sealing means including a sealing bushing mounted on one of said tubular members near the free end thereof, support ring means in sliding engagement with said sealing bushing `and with walls of said casing portion, "and supporting means including a oating ring, a rst pair of pins connecting said floating ring with said sealing `bushing for turning movement about a tirst axis, and a second pair of pins connecting said floating ring with said casing portion -for turning movement about a second axis perpendicular to said rst axis, said first and second axes being perpendicular to the axis of rotation of said rotor means; and said casing portion being formed with diametrically disposed slots extending in the inner surface thereof parallel to said axis of rotation yand receiving said second pins to permit limited axial movement of said tioating ring and sealing bushing caused by displacements of said tubular members.

9. In a fluid handling machine, in combination, rotor means having an axis and including a main portion with a iirst diameter having a circular row of circumferentially spaced working chambers expanding and contracting during rotation, and inlet ducts and first and second outlet ducts communicating with said working chambers, said first outlet ducts extending in radial direction, and said second outlet ducts extending slanted to the radial and axial directions, said rotor means having a fluid distribut ing portion projecting in axial direction from one axial end of said main portion and having a diameter smaller than the diameter' of said main portion, said distributing portion rotating with said main portion and including a plurality of tubular members coaxial with said axis surrounding each other and forming in and between each other an inlet passage connected with said inlet duct and two delivery passages respectively connected with said rst and second outlet ducts; and a stator supporting said rotor means for rotation about said axis, and including a casing portion surrounding said distributing portion and forming with the same an inlet chamber having an inlet, and a plurality of discharge chambers each of which has an outlet, said inlet passage having an opening in said inlet chamber, and said delivery passages having openings, respectively, in said discharge chambers whereby the fluid pressures in said delivery passages and at said outlets of said discharge chambers arel determined by the pressures in the working chambers with which said rst `and second outlet ducts yare connected.

10. In a huid handling machine, 'according to claim 9 wherein said rotor main portion is formed with a plurality of ring channels respectively connecting said delivery passages with said rst and second outlet ducts.

References Cited by the Examiner UNITED STATES PATENTS 1,988,213 1/1935 Ott 103-120 2,452,470 10/1948 Johnson 103-2 X 2,525,498 10/.1950 Naylor et al 103-162 2,601,830 7/1952 Berlyn et al 103-162 2,741,188 4/1956 Wemhones 103-162 2,789,515 4/1957 Smith 103-161 2,859,702 11/1958 Cotner 103-162 2,945,444 7/ 1960 Leissner 103-2 3,070,377 12/ 1962 Eickmann 277-74 FOREIGN PATENTS 1,343,916 10/1963 France.

MARK NEWMAN, Prmaly Examiner.

LAURENCE V. EFNER, DONLEY J. STOCKING,

SAMUEL LEVINE, Examiners.

J. C. MUNRO, W. L. FREEH, Assistant Examiners. 

1. IN A FLUID HANDLING MACHINE, IN COMBINATION, ROTOR MEANS HAVING AN AXIS AND INCLUDING A MAIN PORTION WITH A FIRST DIAMETER HAVING A PLURALITY OF CIRCUMFERENTIALLY SPACED WORKING CHAMBERS EXPANDING AND CONTRACTING DURING ROTATION, AN INLET DUCTS AND OUTLET DUCT COMMUNICATING WITH SAID WORKING CHAMBERS, SAID ROTOR MEANS HAVING A FLUID DISTRIBUTING PORTION PROJECTING IN AXIAL DIRECTION FROM ONE AXIAL END OF SAID MAIN PORTION AND HAVING DIAMETER SMALLER THAN THE DIAMETER OF SAID MAIN PORTION, SAID DISTRIBUTING PORTION ROTATING WITH SAID MAIN PORITON AND INCLUDING A PLURALITY OF TUBULAR MEMBERS SURROUNDING EACH OTHER AND FORMING IN AND BETWEEN EACH OTHER AN INLET PASSAGE CONNECTED WITH SAID INLET DUCT AND A PLURALITY OF DELIVERY PASSAGES RESPECTIVELY CONNECTED WITH SELECTED OUTLET DUCTS WHEREBY THE FLUID PRESSURES IN SAID DELIVERY PASSAGES ARE DETERMINED BY THE PRESSURES IN THE WORKING CHAMBERS WITH WHICH SAID SELECTED OUTLET DUCTS ARE CONNECTED. 